Coil spring and coil spring assembly, including the support for such springs



Sept. 2, 1952 B. LERMONT ,609,

COIL SPRING AND IL SPRING AS BLY, INCLUDING SEM THE SU RT FOR SUCH SPRINGS Filed May 28, 1949 5 Sheets-Sheet 1 Sept. 2, 1952 B. LERMONT 2,609,

COIL SPRING AND IL SPRING ASSEMBLY, INCLUDING THE suc SPRINGS SU RT FOR H Filed May 28, 1949 5 Sheets-Sheet 2 BASIL LERMONT Sept. 2, 1952 B. LERMONT COIL SPRING AND COIL SPR 2,609,192 ING ASSEMBLY, INCLUDING THE SUPPORT FOR SUCH SPRINGS Filed May 28, 1949 5 Sheets-Sheet 3 Filed May 28, 1949 Sept. 2, 1952 B. LERMONT COIL SPRING AND COIL SPRING ASSEMBLY, INCLUDING THE SUPPORT FOR SUCH SPRINGS 5 Sheets-Sheet 4 awe/WM.

Sept. 2, 1952 B. LERMONT 2,609,192

COIL. SPRING AND COIL SPRING ASSEMBLY, INCLUDING THE SUPPORT FOR SUCH SPRINGS Filed May 28, 1949 5 Sheets-Sheet 5 I36 /97 ;go

L 202- '56 -204 1, g l my /82 I I54 i. L93 I90 ,/8/ awe/Mom.

BASIL LERMONT Patented Sept. 2, 1 952 COIL SPRING AND COIL SPRING ASSEMBLY, INCLUDING THE SUPPORT FOR SUCH SPRINGS Basil Lermont, New York, N. Y., assignor, by mesne assignments, to Eastern Metals Research 00., Inc., New York, N. Y., a corporation of New York Application May 28, 1949, Serial No. 95,956

19 Claims.

This invention relates to improvements in coil springs and spring assemblies, and it relates particularly to coil springs which are characterized by equal resistance to straightening (constant tension) .at all zones along the length of the springs.

This is a continuation-in-part of my application Serial No. 747,189, filed May 10, 1947, now abandoned.

It has been usual heretofore in the production of spiral springs and other types of springs to twist or wind a strip of metal on a mandrel or cylindrical form to bend the spring into a desired shape. This coiled strip of metal is then tempered or otherwise treated to render it resilient and to fix or set its normal shape. Due to the method of formation of such spiral springs, each increment of the spring assumes a slightly different radius of curvature in conformance with its initial state of winding with the result that the force required to straighten any given increment differs from the force required to straighten all the other increments of the spring.

It has also been usual heretofore in spring forming machines, to bend wire stock on a constant radius and to employ a skew or pitch memher to continuously deflect the bent material axially into a helix, rather than to allow the material to coil tigthtly upon itself into a spiral with its convolutions disposed in a substantially common radial plane.

It has been further suggested heretofore that coils of metal tinsel strip and other articles can be formed by drawing a'strip of metal over a sharp edge to bend the strip and cause it to coil into generally helical form. Such coiled tinsel strips are commonly used in the production of scouring pads which are used for cleaning kitchen utensils and the like. It appears that the tendency of the strip to form a helix rather than a spiral arises because the strip is maintained under tension while it is drawn over the produce a self-winding coil spring, each increment of which is purposely bent on the same radius of curavture and/or-on a predetermined varying radius of curvature, and which is essentially constant in its resistance to straightening or unwinding throughout its entire length, so that the spring acts much in themanner of a counterweight when suitably assembled with a support or mounting, rather than as a member of variable tension throughout its length.

In accordance with the present invention, such a constant tension spring, that is, a spring every increment of which requires an equal force to straighten it, is produced by drawing or passing a strip of metal between two forming elements to bent the strip partially so that every increment of the spring is bent on an equal radius and so the convex surface portion is stretched while the concave surface portion either is unstretched or actually is compressed slightly. Due to the uniform deformation of the strip, every increment of it is stressed equally and it will tend to coil into one or more convolutions each of which has the same radius of curvature when unrestrained.

When such a spring is mounted so that it can turn freely and a force is exerted on one end of the spring tending to unwind it, it acts very much like a counterweight for the reason that any tension applied to the spring will tend to straighten that portion which is tangent to the outer surface of the coiled portion of the spring. Inasmuch as every increment of the spring is equally stressed and bent, the force required to straighten any given portion of the spring is exactly the same as the force required to straighten any other portion of the spring. Therefore, the resistance to straightening or drawing out of the spring is not cumulative. That is to say, a force strong enough to straighten or unwind one end of the spring will, if continuously applied, completely straighten out or unwind the entire spring, assuming, of course, that the convolutions or coils of the spring are all allowed to assume their normal state. Thus, a sprin which has been formed with a predetermined constant radius of curvature and is equally stressed throughout, if allowed to form itself into a plurality of independent coils or convolutions in which each coil is not obstructed or distorted by contact with other convolutions, will have the above-mentioned constant tension characteristics. On the other hand, if the spring is allowed to coilv upon itself, that is, to coil into a tightly wound spiral, the constant tension characteristics are modified by the following factors. It is evident that no two of the convolutions, even if equally bent, can occupy the same space. As a result, one or both of the convolutions must flex to different curvatures from their normal constant radius of curvature. Therefore, when a straightening force is exerted on the free end of the spring, a greater or lesser straightening will result as the spring unwinds, and the force required to straighten the spring will vary accordingly.

Also, in the case of a spirally coiled but constant radius spring, the radius or moment arm of the force acting on the spring becomes less and less as the Spring is unwound, thereby requiring an increasin force to unwind the spring To overcome the effects of the varying moment arm and the partial straightening of the spring because of space limitations, in spirally coiled springs, the spring can be modified either by varying the resistance to straightening throughout the length of the spring, for example, by varying its radius of curvature throughout so that the outer end portion of the spring normally tends to curve (when in repose) on a shorter radius than its inner end portion, or by tapering or perforating the spring throughout its length. These variations in the spring should be such as to just offset or compensate for the change in deflection of the spring and the change in the length of the moment arm of the spring as it coils and unccils.

The term when in repose, as used herein, refers to the condition of the spring as initially set on any given radius, either constant or varying, by the bending operation itself. In other words, the term when in repose refers to the condition of the spring free of additional stresses such as are imposed, for example, by mounting a spring upon a supporting member of greater radius than the given radius of the portion of the spring engaging said supporting member or by spiral winding or other disposition of the convolutions of the spring in a manner requiring any convolution to assume any radius different from that upon which it was originally set.

The forming devices disclosed herein are capable of producing springs formed with any desired constant radius or with any desired varying radius. The radius of curvature of the spring can be modified by adjusting the sharpness or abruptness of the bending of the spring material, and in order to accomplish this function, different anvil blocks or die members, having different radii of curvatures may be used, or an anvil member of a fixed curvature but having a cooperating adjustable retainin or hold-down member for altering the width of the gap between the two members to correspondingly vary the radius of bending of the strip, may be provided.

The manner in which the strip is passed through the gap between the die members may be varied. Preferably, the strip is drawn over the die member without any tension being exerted on the trailing end of the strip. If the strip is of sufficiently heavy gauge, it may be forced over the anvil or die member by means of suitable feed rollers so that the strip is not maintained under tension during its forming operation.

The principal object of the present invention is to provide springs having constant tension characteristics, and methods and apparatus for producing such springs.

Another object of the invention is to provide a spring having increments thereof bent upon a constant radius of curvature and/or a varying radius of curvature.

Another object of the invention is to provide a coil spring which requires a predetermined force to unwind any predetermined part of its length.

Another object of the present invention is to provide constant tension springs and spring assemblies of the type referred to hereinabove.

For a better understanding of the present invention, reference may be had to the accompanying drawings, in which:

Fig, 1 is a diagrammatic perspective view of a typical form of apparatus for making springs of the type embodying the present invention;

Fig. 2 is a view in section through the die or forming elements taken on line 22 of Fig. 1;

Fig. 3 is a perspective view of a coil spring of a character which can be formed by the apparatus illustrated in Figs. 1 and 2;

Fig. 4 is a diagrammatic illustration of a modified form of spring-forming device il'lVOlVll'lg the use of feed rollers for pushing the strip through the die gap;

Fig. 5 is a diagrammatic view illustrating the relationship between a piece of spring material and a pair of dies, such as shown in Fig. 4, during the bending operation on the spring material to form it into a coil spring;

Fig. 6 is a perspective view of a constant tension spring which can be made by the apparatus of Figs. 4 and 5, the spring, however, being shown assembled with a support;

Fig. '7 is a perspective View of a spring in which all increments thereof are bent upon a given constant radius;

Fig. 8 is an elevational view of a spring of the type shown in Fig. 7, wherein portions of the spring are wound in reverse directions;

Fig. 9 is a diagrammatic view illustrating one practical application of the constant tension spring shown in Fig. 8;

Fig. 10 is a perspective view of a spring which is perforated to modify its tension characteristics to compensate for variations in the moment arm and inability of a plurality of convolutions of the spring to occupy the same space;

Fig. 11 is a perspective View illustrating another practical application of the present spring, wherein the spring is supported on a rotatable shaft or arbor for producing a constant tension effect;

Fig. 12 is a perspective View of a modified form of mounting for a spring having constant tension characteristics;

Fig. 13 is a perspective view illustrating another form of spring assembly having constant tension characteristics;

Fig. 14 is a diagrammatic perspective view of a modified form of apparatus including a control cam for automatically making constant tension springs having a uniformly varying radius of curvature;

Fig. 15 is an elevational View of another spring assembly including a spring, which may be formed on a constant radius by the apparatus shown in Fig. 4 or formed on a progressively varying radius by the apparatus shown in Fig. 14, adapted to serve as a counterbalance for a window sash (not shown);

Fig. 16 is an elevational view of a modified cam adapted for use in the apparatus shown in Fig. 14 to automatically form a spring having the opposite end portions thereof bent upon different constant radii and an intermediate portion bent upon a varying radius;

Fig. 17 is a schematic elevational view of a spring that can be produced by substituting the cam shown in Fig. 16 for the cam presently shown in Fig. 14;

Fig. 18 is a diagrammatic view, partlyin crosssection, of another-form of automatic machine for bending spring material upon any desired radius of curvature, either constant and/or progressively increasing .or decreasing;

Fig. 19 is a detail sectional view taken on the line l9l9 of Fig. 18;

Fig. 20 is a plan view of the automatic machine shown in Fig. 18;

Fig. 21 is a detail sectional view taken on the line 2l-2l of Fig. 20;

Fig. 22 is a diagrammatic view illustrating one form of driving mechanism for the machine shown in Figs. 18 to 21;

Fig. 23 is a diagrammatic view illustrating a cam and other elements associated with an electrical circuit for automatically controlling the machine;

Fig. 24 illustrates a modified form of cam adapted to be substituted in the control mechanism show in Fig. 23 to form a spring having the end portions thereof formed on uniformly varying curvature and the intermediate portion thereof bent upon a constant radius; and

Fig. 25 is a schematic view of a coil spring that can be formed under the control of the cam shown in Fig. 24.

The apparatus described hereinafter is typical of the many different forms ofdevices by means of which springs of the type embodying the invention can be produced and, therefore, should be considered as illustrative only.

Referring now to Fig. 1, a simple form of apparatus for forming springs of the type embodying the present invention may consist of a base member I which may take the form of a block of reinforced concrete or a metal beam having at one end an upstanding lug H to which the cylinder 12 of a hydraulic jack is fixed by means of a pivot pin l3 extending through the clevis M at the end of the cylinder and through the lug l I.

The piston rod I5 of the cylinder is provided with a pair of pivotally connected gripping jaws l5 and I! having suitable hand screws [8 and I9 therein for forcing the blocks I6 and I! together to grip the end of an elongated piece or sheet of flexible metal 20, from which a spring is to be formed. The sheet 20 can be any of the conventional types of spring steel or an alloy, such as a beryllium-copper alloy. It may even be formed of stainless steel which has been found to have excellent spring properties when treated in accordance with the present invention.

The opposite end of the base member H1 is provided with an anvil block or lower die member 22, which, as best shown in Fig. 2, may consist of a bar of metal having parallel opposite sides 22 and 22', a lower side 22 which is perpendicular to the sides 22* and 22 and an upper side 22 which is inclined at an acute angle to the side 22*. The junction of the sides 22 and 22 is curved to form a generally arcuate or rounded convex surface 22 of a radius of curvature which is dependent upon the desired radius of curvature of the spring being formed, as will appear more fully hereinafter.

The strip 20 passes over the rounded surface 22 and is bent into conformity with the shape of this surface by means of a second die block or hold-down member 23. This hold-down member preferably is provided with a recessed undersurface having a concave surface portion 23 which is concentric with the surface 22 On opposite sides of the concave surface 23 are right angularly related surfaces 23 and 23 which engage the outer surface of the strip 20 and aid in bending it around the surface 22 The shape of the upper and lower die blocks 23, and 22, respectively, asidefrom the relationship of the surfaces 22 22 and 22 and the surfaces 23*, 23 and 23, is unimportant.

The two blocks 22 and 23 are retained in their desired relationship by means of the stud bolts 24 and 25 at opposite ends of the die members 22 and 23. The lower end of the stud bolt 24 is anchored in a lug 26 on the end of the die block 22 while the upper end passes through an opening in the upper member 23 to receive a nut 21 for clamping the two die members together. The stud bolt 25 is similarly mounted at the opposite end of the die block 22 and is provided with a nut 28 for holding the die members 22 and 23 in contact with the sheet 20.

In operation, the piston rod I5 is advanced by admitting fluid into the cylinder [2 through the conduit 30 until the gripping plates l6 and Il are closely adjacent to the die block 22 and the end of the sheet of metal 20 is threaded through the gap G between the die blocks 22 and 23 while they are spread apart a greater distance than the thickness of the sheet. The end of the sheet is then clamped between the gripping plates [6 and H, and the upper die block member 23 is tightened down by adjustment of the nuts 21 and 28 until the portion of the sheet 20 between the die blocks is bent into conformity with the curvature of the forming surface 22 Pressure is then applied to the cylinder I2 through the conduit 30 to draw the sheet 20 over the curved forming edge 22 thereby bending the sheet sharply and stretching the outer portion of the sheet. Such stretching imparts a permanent set to the metal, and when the free trailing edge of the sheet finally passes by the forming edge 22, the sheet will coil tightly upon itself with its convolutions disposed in a substantially common radial plane to form the spring S shown in Fig. 3. The drawing action of the cylinder,- while having some tendency to straighten the sheet 20, has been found to act equally throughout the length of the sheet so that while its radius of curvature R is considerably greater than the radius of curvature of the forming surface 22 the amount of curvature throughout the length of the bent portion of the sheet is exactly the same for any increment thereof. The end 20' of the strip 23 which was clamped between the jaws It and 1? remains straight, as shown, and may be provided with an opening 20" to facilitate attachment thereof to any object.

Springs of still greater radius of curvature can be produced by loosening the nuts 2'? and 23 separately or simultaneously to permit die blocl: 23 to retract somewhat to increase the width of the gap G so that the sheet 20 is not bent as much as when the block 23 is held down tightly against the upper surface of the sheet. The nuts 2'! and 28 can obviously be manually adjusted while the sheet 20 is stationary, or in motion. Also, interchangeable die blocks may be used in which the radii of curvature of the surfaces 22 and 23 are greater or lesser in order to form springs of different curvatures.

In order to offset any tendency of the cylinder [2 and the piston [5 to straighten the strip or sheet, springs may be produced by forcing, instead of pulling, the strip between die blocks similar to those described above. As shown in Fig. 4, the die blocks 35 and 36 therein may be similar to the die blocks 22 and 23. The lower die block 35 is supported in a suitable frame, not

7 shown, which also supports a pair of driven feed rollers 31 and 38.

The elongated piece or sheet of metal 39 is gripped between the rollers 31 and 38, which are positively driven in opposite directions by means not shown, to force the sheet 39 between the die block members 35 and 36 so that the sheet will be bent as described above and will form a tight coil at the discharge end of the die blocks 35 and 36.

In forming coil springs with the apparatus shown in either Figs. 2 or 4, it is generally preferable to have the die members 23 and 36 spaced from the die members 22 and 35, respectively, a distance somewhat greater than the thickness of the material which is passed therebetween. The width of the space or gap between the dies 35 and 36, as indicated by the dimension G in Fig. 5, will vary with the character and thickness T of the spring material. The draw radius r, or radius of curvature of the rounded edge 22 of the die member 22 and the corresponding edge of the die member 35, will also vary with the character and thickness of the spring material. Assuming that the spacing or gap G between the die members is not adjusted during a springforming operation, then the radius R, will be constant for any increment a, a", or a! of the spring material passed between the die memhere. The bend radius, of course, can be varied by increasing or decreasing the dimension of the gap G so that coils having any predetermined constant or varying radius of curvature can be produced, as desired.

The radius of curvature R will also be predetermined in the light of practical consideration by proper design of the die members with due consideration being given to the kind of material employed and its dimensions, as will appear hereinbelow. I

For most purposes, resilient, cold rolled strip material is preferred. By way of operative examples, the springs may be made of high carbon strip steel,'S. A. E. No. 1095 having a Width of and a thickness of (.016). When this particular material is used, it is preferable to use a die block in which the draw radius r is i g" or .0625, and the gap G between the die blocks is .038". Each resulting coil will then tend to assume a normal diameter of 1%" or 1.375, with each successive increment of the spring bent upon a constant radius R. Such a spring has been found to require a constant force of only 66 ounces, or 4 lbs. and 2 ounces, to eiiect unwinding thereof regardless of the number of convolutions that are unwound.

As a further operative example of the invention, the springs may be formed of a strip of stainless steel having a thickness of .011" and a width of 1'. In coiling such material, the draw radius r on the die block is preferably or .156 and the gap G between the die blocks is preferably .016". The resulting coils will then have a normal diameter of 19 with each increment bent upon a constant radius of curvature R. The load tension capacity of such spring is 60 ounces, or 3 and 4 lbs.

The cross-sectional shape of the material from which the spring is formed can be varied substantially. Thus, the spring can be formed of wire or the like, of circular, square or triangular cross-section or from thin strip material and: the like of any suitable width.

The spring material, 39- may be iediiromasupply roll (not shown) or consist of strips of predetermined length, which may be bent upon a constant radius throughout to form a coil spring 3*, as illustrated in Fig. 7. On the other hand, a predetermined length of the material 39 may be bent upon a constant radius and a portion left unbent to provide a spring S having an end 39 which is in a straight condition, as shown in Fig. 6. In the event of the latter, the die blocks 35 and 36 are separated when the desired portion of the spring has been bent, so that the end portion 39 of the spring material remains unbent or straight. When the spring material 39 is fed from a supply roll, completed springs can be severed by conventional cut-off means (not shown).

In Fig. 6, the spring S is operatively assembled with supporting means shown in dot-and-dash lines and comprising a drum 39 (to which the inner end of said spring can be secured, if desired) supported upon a shaft 39 rotatably mounted in a bracket 39 The spring shown in Fig. 7 has an inner end W and an outer end X. The latter end may be unwound and then rewound, as illustrated in Fig. 8, to form two coil portions S and In such case, the pressure at the zone of contact of the coils, indicated by the letter Y, will be substantially constant irrespective of the number of convolutions comprising the respective coil portions S and S As illustrated, each coil portion S and S comprises two convolutions, the outermost of which are inherently urged toward each other by a force efieetive at Y. The force at Y would be substantially the same if one of the coil portions had only one convolution and the other had three.

Fig. 9 diagrammatically illustrates one practical application of the type of coil spring shown in '7 and 8. Here, the end X of the spring is wound around a roller M rotatably mounted upon a pin P carried between the arms of a yoke A. The opposite end W of the spring is wound around a similar roller M rotatably mounted upon a pin 1? carried by another yoke A. The arms A and A are connected together by means of a cable or cord C which is looped over the pulleys or rollers R, R. and passes below them so that the spring continuously tends to move the rollers M and M toward each other. Such movement is opposed by a load L acting downwardly at the mid-point of the cabl C, the net result being that the rollers can be maintained spaced apart any desired distance without increasing th load L. It will be obvious from this illustration that the constant tension spring. S may be used in any environment where it is desired to maintain a constant tension on two elements even though the distance between the parts is required to be varied from time to time.

Should the springs S and S shown in Figs. 3 and 6, respectively, be used in their coiled condition, the moment arm of successive convolutions will vary, s that the force required to unwind the springs will increase as the springs are unwound and their moment arms become shorter. Compensation in the way of a correction factor may be made for moment arm variations andtrue constant tension characteristics provided by varying the bending radius the required amount during fabrication. Alternatively, spring material of tapered width and/or thickness may be employedv so the moment arm times the force required to unwind any increment of the spring equals a constant.

Compensationv for variation in the length of the moment arm of the force required to straighten ortendingto rewind the spirallycoiled spring can also behad by perforating the spring material in such 'a way as to render the outer end of the spring less resilient than the inner end. Thus, as shown in Fig. 10, the partially uncoiled spring 8'' has aseries of perforations 60 therein. These perforations are spaced apart gradually decreasing distances from the outer end of the spring to the inner end of the spring. This latter variation of the spring is difficult to practice in mass production operations, as is the production of tapered springs, and therefore, these modifications are the least preferred modifications.

It appears that the constant tension characteristics of preferred types of springs arise largely from the act that the portion of the spring being bent by the dies and 36 is not maintained under tension, and the spring is merely bent, rather than stretched, during its formation. Because of the'lack of stretching, which would cause elongation of the spring material during its formation into the spring, there is no tendency for the spring to develop weak zones at its center or along its edges, which would vary the coiling characteristics of the spring.

Assuming that the above-described springs are bent on the same radius of curvature, each convolution thereof normally tends to form a circle of the same diameter. However, inasmuch as all of the convolutions of the spring cannot occupy the same space, the spring must initially form a spiral with the convolutions in contact and pressing against each other.

Springs of the type produced in accordance with the method and apparatus described above can be duplicated in quantity and with a high degree of accuracy in their characteristics. These springs are uniform in their characteristics throughout and are especially suitable for use where a uniform. tension is required from the spring regardless of the amount that the spring is extended. Thus, when the spirally coiled spring S is .drawn out endwise into helical form, as shown in Fig...ll, and one end of the spring, which may be either end, is secured to a rotary shaft or other member 40 mounted in supports 40 the free endof the spring may be drawn out to unwind the spring by the application of a uniform force thereto. The force applied need not exceed that required to start the spring unwinding, to completely unwind the spring. The spring, therefore, acts very much like a counterweight of fixed value in any of its wound, partially wound or. unwound states. Thus, the spring exerts as much tendency to wind up or coil at its inner end as it does at its outer end, and therefore, compensation need not be made for the extent of unwinding of the coil as is common in the conventional spiral coil springs. The same results are obtainable if the shaft 40 is omitted and the spring is mounted in such a way as to permit free. body rotation of the spring as one of its ends is drawn out.

As shown in Fig. 12, a spring S of helical form, like the spring S described above, may be mounted loosely in a cylindrical receptacle 4| having a slit 42 in one wall through which one end 43 of the spring extends. When a force of sufficient magnitude is exerted on the end 43 of the spring S, the spring will rotate bodily in the receptable 4| permitting the spring to unwind. Upon release of the force, the spring S will wind itself upin the receptacle either as a helix or as a group of convolutions of'equal radius. These convolutions do not necessarily assume a helical shape and advantage can be taken of this fact to permit a very long spring to be mounted in a relatively small'space, as shown in Fig. 13. For example, a long, slender spring 8" bent on a uniform radius of curvature willv have constant tension characteristics if permitted. to coil loosely or at random into a series of convolutions of generally ball-like shape. If this ball-lik mass is mounted for free rotation in a hollow, box-like receptacle 44, the spring S may be drawn out through a slot 45 in the receptacle, thereby uncoiling the spring. Release of the withdrawn end of the spring will permit it to coil up again into the loose ball-like shape.

While the springs of uniform radius of curvature cannot provide truly constant tension characteristics when usedas spirally coiled springs, it is possible to modify the characteristics of such spirally coiled springs to provide the desired constant tension characteristics when mounted in the manner described above, that is, for free rotation of the spring as a whole. This may be accomplished, as stated, by using tapered stock (width and/or thickness) which, when bent on a constant radius, will have the larger section at the outer end of the coil. The larger sectional area and the consequent greater resistance to straightening offsets or compensates for the longer moment arm through which the applied force acts to straighten and unwindthe spring. It also compensates for the partial straightening of the spring due to the inability of all of the convolutions to occupy the same space.

Generally, the same elfect'may be producedby bending the spring on a uniformly varyingradius so that the outer end is bent on the shortest radius and the inner end is bent on the longest radius. This effect can be obtained with my above-described apparatus by careful manual adjustment of the die, elements 2223 and 3536, while the spri g, is being formed, but it is preferable to provide a modified automatic apparatus which will constantly vary the gap between the upper and lower die elements during a forming operation.

A typical apparatus for this purpose is shown in Fig. 14. This apparatus includes the same general arrangementof die or forming elements 59 and 5| as those shown in Figs. 1 and 4. Instead of employing the, clamping bolts and nuts shown in these figures, the modified device is provided with guide'rodsjz and 53 which carry springs 54 and 55. These springs normally'urge the forming members 50 and 5| apart.

A cam 56 is provided with a peripheral portion 51 which uniformly, decreases in radius in a counterclockwise direction from a point 58 toa point 59 and has a depression 60 between said points. The cam 56 is engaged with a roller 6! carried by a pin 62 mounted in lugs 63 formed on the die member 5|. The cam portionil is designed so that it gradually moves the die member 5| toward the die member 50 as the cam is rotated. This results in bending successive increments of the spring material 64 on a progressively decreasing radius of curvature, so that the inner end of the spring thus formed has a greater radius of curvature than its outer end and the force required to straighten any increment of the spring is the same for all increments, regardless of changes in the. physical length of the moment arm. When the depression, 65 is engaged with the roller 6|, the die members 59, 5| are permitted to move apart their maximum distance under the action of the springs 54, 55. Reversing the cam, or reversing its direction of rotation, will result in a coil spring having its outer end portion bent upon a greater radius of curvature than its inner end and such spring may be useful for certain purposes.

The cam 56 may be mounted on a shaft 65, which is supported in bearings 66 and 6'! and rotated by means of reduction gearing including a gear 68 driven at a desired speed in timed relation to the rate of movement of the spring material 64 between the dies 50 and The spring material 64 can be fed by feed rolls such as the feed rolls 3'! and 38 shown in Fig. 4, or pulled by a rod I5 and cylinder I2 such as shown in Fig. 1.

By suitably shaping the cam 56, the spring can be provided, during its formation, with a uniformly varying curvature, or with a varaible or irregular curvature, depending upon requirements. If the drive to the gear 68 is interrupted, the cam 56 can then be manually adjusted to a fixed position to maintain the die member 5| in fixed relation to the die member 50 to form a spring having any desired constant radius of curvature.

Adjustment of the member 5| may also be used to compensate for variations in the thickness of the material being formed into a spring. For example, strip or wire stock may vary in thickness due to errors in forming it, so that even a constant radius spring formed from such stock may actually vary somewhat in its spring characteristics. Thi variation can be overcome by determining the variations in thickness and forming the spring on a correspondingly varying radius of curvature.

Fig. 15 illustrates a constant tension spring embodying the principles of the present invention, associated with support mean for enabling the same to function as a counterbalance, for example, for a window sash (not shown). Here, the spring S is wound upon the outer periphery of a drum 1|] rotatably mounted upon a pin 1| carried by a bracket 12. The bracket 12 comprises a base portion 13 and flanges I4 and 15 extending upwardly from the longitudinal edges thereof. The pin H is mounted in the flanges 14 and I5 and serves as a shaft supporting the drum for free rotation relative thereto.

The radius of the drum 10 is preferably greater than the radius upon which the spring has been bent so that the inner convolutions 15 of the spring, in tending to assume its normal diameter, tightly grips the outer periphery of the drum. The end H of the innermost convolution 16 need not be interengaged with or fastened to the drum 10 in any manner. The free end 13 of the spring extends through an opening 19 formed in the bracket base 13 and said lower end may be perforated or suitably shaped for attachment to a window sash (not shown).

Inasmuch as the resistance offered to unwinding of the spring is not cumulative, the force required to unwind or straighten any given increment of the spring S is the same for all other increments of the spring. Variations in the length of the moment arm for successive convolutions of the spring, as the spring is being unwound, can be compensated for by employing a spring which has its successive increments bent upon a variable radius.

In the case of a window counterbalance, the spring selected will be such that it will unwind when a pulling force of only a few ounces is ap- 12 plied so that very little physical efiort is required to unwind the spring to effect lowering of the sash. On the other hand, the spring inherently rewinds itself as the sash is raised and, in this way, substantially counterbalances the weight of the sash so that only a very small physical force again need be applied to raise the sash.

Fig. 16 illustrates a modified form of cam 55* which may be substituted in the apparatus shown in Fig. 14 for the cam 56. This cam includes a peripheral portion 80 defined by an are a of constant curvature and another portion 8| defined by an arc bof constant curvature, but less than that of the portion 86. A portion 82 defined by an are c of uniformly varying curvature is disposed between the portions 80 and 8|. The remainder of the cam-56 is defined by a portion including a pocket or depressed region 84 adapted to cooperate with the roller 6| upon the holddown or die member 5| to permit maximum separation of the die members 50 and 5|.

It will be apparent that when the cam 56 is mounted upon the shaft 65 and rotated in the direction indicated by the arrow, and the portion 80 is engaged with the roller 6|, the die member 5| will be maintained in fixed spaced relation to the die member 50 so that the spring material then passing between the dies will be bent upon a constant radius. When the portion 82 of the cam is engaged with the roller, the die member 5| is permitted to gradually slide upon the rods 52 and 53 in a direction away from the die member 5| to progressively increase the width of the gap between the die members 50 and 5| and thereby cause the portion of the spring material then passing between said die members to be bent upon a varying, progressively increasing radius. As the cam 56* continues to rotate, the portion 8| will contact the roller 6| and again maintain the die members 50 and El in fixed spaced relation, but with the gap wider than when the cam portion 80 was engaged with said roller. The spring material then bein passed between the die members 50 and 5| will be bent upon a constant radius, greater than the radius R. A spring thus formed is diagrammatically illustrated in Fig. 17 and generally identified by the letter S It will be noted from this figure that the inner convolutions 85' of the spring are formed upon a constant radius R, whereas the outer convolutions 86 of said spring are formed upon a relatively greater constant radius indicated by the letter R. The intermediate convolutions 81 of the spring 84 are bent upon the constantly varying radius R1), which progressively increases from the radius R to the radius R. Reverse mounting or reverse driving of the cam 55 will result in a spring having its convolutions bent in the reverse relation from that described above.

It will be apparent that by varying the contour of the cams 56 and 56a, a spring having any desired tension characteristics, constant or otherwise, can be automatically formed, and such desired characteristics can be accurately reproduced in the successive springs formed by the machine with any given cam design.

Figs. 18 to 23 illustrate still another form of machine for automatically coiling springs which embody the principles of the present invention.

Referring now more particularly to Fig. 18, the machine comprises a bed plate I00 supported upon frame members |0| at opposite edges, only one of said frame members being shown in the drawing. A bracket I02 is adjustably secured to the underside of the bed plate by machine bolts I03 and serves as a journal'for a shaft I04 having a feed roll I05 secured thereto. A similar feed roll I06 is secured to a shaft II rotatably mounted in a bracket I08, which, is also adjustably secured to the bed plate I00 by bolts I09. The brackets I02 and I08 carrying th feed rolls I and I06 are so adjusted that said feed rolls engage the spring material I00 with sufficient pressure to force the same through a pair of bending dies H0 and III, which have confronting faces similar to those of the dies 22 and 23.

A guide H2 is interposed between the discharge side of the feed rolls I05 and I06 and the entrance gap G of the die blocks III) and III. The guide II2 comprises a bracket II3 secured to the underside of the bed plate I00 by bolts I I4. The bracket I I3 is provided with a channel H5 (Fig. 19) through which the spring material I00 passes and is guided so that it travels upwardly in a path perpendicular to the forming faces of the die blocks H0 and III. The spring material I09 is retained in the channel II5 by a plate II6 secured to the bracket II3 by screws H1.

The die member I I0 is secured to the bed plate I00 by a plurality of cap screws H8. The cooperating die block or hold-down member III is secured to an inclined platform II9 by a plurality of cap screws I20.

The platform H9 is supported at an angle of about 45 to the horizontal by a pair of guide rods I2 I. The lower end of each guide rod I2I is received in a bracket I22 adjacent one end of the die block IIO. Each of the brackets I22 is secured to the bed plate I00 by cap screws I23. A pin I24 retains the lower end of the guide rods I2I in the brackets I22 and holds said rods against rotation. The upper end of each guide rod I2I is received in and supported by a bracket I25 secured to the bed plate by cap screws I26. The guide rods I2I extend through an opening I21 extending transversely through the platform H0 and the intermediate portion of each guide rod I2I is provided with threads I28. The platform I19 is provided with longitudinal slots I20 each of which intersects one of the openings I21. An internally threaded travelling nut I30 is disposed in each of the slots and is engaged with the threads I28. Each of the nuts I30 is keyed, as best shown in Fig. 21, to a worm wheel I3I, which is also disposed in each of the slots I29.

A reversible, constant speed electric motor I32 is mounted upon the platform H9 by bolts I33, and hasa shaft I34 projecting from each end thereof. A worm I35 is secured to each end of the shaft I34 and meshes with one of the worm wheels I3I. A conventional, electrically operated brake I36 is suitably mounted upon the platform H9 and is adapted to cooperate with the shaft I34 to prevent overrunning thereof at such time when the current to the motor. I32 is cut off, all as will be explained more fully hereinafter.

It will be apparent from the foregoing that when the motor I32 is rotating in one direction, say forward, the worms I35 will cause the worm wheels I3I to turn and thus rotate the travelling nuts I30 to cause the platform IIO to travel along the guide rods I2I in a direction toward the die block IIO, thereby moving the hold-down member III toward said die block and decreasing the width of the gap therebetween. On the 14 other hand, when the motor I32 is rotated in the opposite, or reverse, direction the worms I35 will rotate the worm wheels I3I in the opposite direction and cause the platform II9 to travel along the guide rods I2I in a direction away from the die block IIO, thereby increasing the width of the gap between said die block and the holddown member I II. The pitch of the threads I28 and the drive ratio of the worm I35 and the worm wheel I3I are designed so as to move the hold-down member III relative to the die block IIO to bend the spring material I09 upon any constant or varying radius desired, so that the finished spring will have any tension characteristics desired.

The travel of the platforms II9 carrying the hold-down member III may be controlled in any number of different ways. However, for illustrative purposes, one form of operative automatic, electric control means is illustrated and described herein. The control means is conveniently mounted upon a stationary platform I40 suitably secured to the machine legs I0 I. Bracket means MI is mounted upon the platform I40 and rotatably supports a shaft I42. A control cam I43 is secured to the shaft I42 so that it is driven thereby. A roller I44 engages the periphery of the cam I43 and is rotatably mounted upon a pin I45 mounted in an arm I46. The arm I46 has one end thereof pivotally supported by a pin I48 mounted in one of the legs IOI. A spring I49, which may be a constant tension spring embodying the principles of the present invention, has the coiled portion thereof engaged with an offset in the arm I46 and one end thereof is secured at I50 to a rod I5I mounted on the platform I40. The spring I49 thus constantly urges the roller I44 into contact with the periphery of the cam I43 under a constant pressure.

An upright rod I52 has its lower end threaded and mounted in a threaded opening I53 formed in the platform I40. A block or frame member I54, preferably formed of electrical insulating material, is adjustably secured to the rod I52 by a set screw I55, the portion of the rod I52 engaged by the frame I54 being rectangular in cross-section so that said frame cannot turn relative to said rod. The frame I54 includes an upper arm I58 having a conventional, normallt open Micro switch I51 mounted thereon, and a lower arm I58 having a similar switch I50 mounted thereon.

The arm I46 carries a flat spring member I60 provided with an insultaed double contact I6I. The contact I BI is adapted to engage with a contact I62 on a c-shaped conductor mounted on the frame I54, or with a similar contact I63 on said conductor, depending upon which portion of the cam I43 is engaged with the roller I44. The contact I6I has an intermediate position in which it is engaged with neither contact I62 nor I63 and at such time the circuit to the motor I32 is interrupted, as will appear more fully hereinafter. However, the spring strip I60 is arranged so that it is adapted to engage and actuate the sensitive operating pin I64 of the Micro switch I 51 shortly after the contact I6I has engaged the contact I62, and to likewise engage and actuate the sensitive pin I65 of the Micro switch I59 after the contact I6I has engaged the contact I63. The reason for this is that the contacts I62 and I63 are associated with relays, which will be described later, adapted to simultaneously release the brake I36 and complete the circuit to the motor I 32, and alternatively, to simultaneously apply said brake and interrupt the circuit to said motor, all as will be described more fully later.

The cam I43 (Fig. 23) includes a portion I19 which is of greater radius than a portion I1I thereof. The cam I43 also includes portions I12 and I13 defined by a radius less than that of the portion I19 but greater than that of the portion Ill. The roller I44 isshown engaged with the portion I12 at which time the contact I6I is in its intermediate position and is not engaged with either the contact I62 or the contact I63. When the portion I19 of the cam is engaged with the roller I44, the contact I6I will be raised into engagement with the contact I62, and when the cam portion IN is engaged with the roller I44, the spring I49 will cause the arm I46 to move in a clockwise direction about its pivot I48 and thus engage the contact I6l with the contact I63.

The electrical control means for the machine further includes a normally closed relay I15 (Fig. 23) and a normally open relay I16, both of which may obviously be mounted upon the platform I 49. The relays I15 and I16 are operated by 6 volt direct current produced by a transformer I11, which may also be mounted upon the platform I49.

Fig. 23 illustrates the manner in which the motor I32, brake I36, Micro switches I51 and I59, the relays I15 and I16, transformer I11, etc., are interconnected in a circuit for automatically controlling the machine. Thus, electric current is supplied to the machine through 110 volt A. 0. main conductors I89 and I6I. Leads I 62 and I 63 connect the conductors I89 and I8I, respectively, with the primary coil of the transformer I11. A Wire I84 connects one side of the secondary coil of the transformer with the contact I6I. The other side of the secondary coil of the transformer I11 is connected by a wire I65 to the relay I15 whose contacts I86 and I81 are normally closed. Another wire I86 extends from the relay I15 to the relay I16 whose contacts I99 and I 99 are nor mally open. Another wire I9I extends from the relay I16 to the contacts I62 and I63. Thus, the relays I15 and I16 are connected in series.

The Micro switch I51 is diagrammatically illustrated as comprising contacts I93 and I94, and the Micro switch I59 is similarly illustrated as comprising contacts I95 and I96. 2

One terminal I91 of the brake I36 is connected with the conductor I89 and the other terminal E98 is connected by a wire I69 with the contact I81 of the normally-closed relay I15. The other contact I86 of the relay I15 is connected by a wire 299 with the other conductor I 9| With the contact IBI intermediate the contacts I62 and I33, as shown, the circuit to the brake I36 is completed through the conductor I99, wire I99, contacts I66 and I31 of the relay I15, Wire 299 and conductor ISI, so that the brake is applied and holds the motor shaft I34 against rotation. This relationship corresponds to the position of the roller I44 when engaged with either of the cam portions I12 or I13 of the control cam I43.

One terminal 29I of the motor I32 is connected by a wire 292 with the contact I69 of the normally-open relay I16, and the other contact I99 of said relay is connected by a wire 293 with the conductor I66. One of the contacts I93 of the switch I51 is connected by a lead 294 with the wire 292 and the other contact I94 of said switch is connected by a wire 295 with a second terminal 296 of the motor I32. The contact I95 of the Micro switch I59 is connected by a lead 291 with the wire 295, and the other contact I96 of said switch is connected by a lead 299 with the conductor I6I, said conductor being connected to a third terminal 299 of said motor.

Assuming that the cam I43 has rotated clockwise to a position such that the cam portion I19 engages the roller I44, the contact I6I will then engage the contact I62, and the circuit to the relays I15 and I16 will be completed so that both relays are energized. The circuit is completed from one side of the secondary winding of the transformer I11 through the wire I95, the coil of relay I15, wire I93, the coil of relay I16, through the wire I9I, contacts I62 and I6I, and back through wire I84 to the other side of said secondary winding. Energization of the relay I15 opens the contacts I86 and I81 thereof, thereby interrupting the circuit to the brake I 36 and releasing the motor shaft I 34 for rotation. The simultaneous energization of the relay I16 causes the contacts I69 and I99 thereof to engage, and the actuation of the pin I64 of the "Micro switch I51 by the spring strip I69 causes the contacts I93 and I94 of said switch to engage and thereby complete the circuit to the motor I32 to drive the same in a forward direction, i. e., to move the die member I II from its fully retracted position toward the die member III) to slowly decrease the width of the gap G, Fig. 18. Th circuit to the motor I32 is then completed through the main conductor I69, relay contacts I99 and I99, and wires 292 and 294, Micro switch contacts I93 and I94, wire 295 to one terminal 296 of the motor I32, and from motor terminal 299 to the other main conductor I6I. With the cam I43 designed as illustrated, the motor I32 will continue to rotate in a forward direction during almost a half revolution of the cam I43 indicated by the angle P. During this period, the platform I I9 will be very slowly moved in a direction toward th die block H9, carrying the hold-down member III with it, so that the gap G between the hold-down member I I I and the die block I I9 very slowly decreases with the result that the radius of curvature upon which the spring material is bent will very gradually decrease as the strip of spring material I99 is passed between said die block and hold-down member. The bending of the spring material I99 will have been completed by the time that the portion I13 of the cam I43 is engaged with the roller I44. At such time, the contact I6I will be returned to its intermediate position and the circuit will then be in the condition initially described, namely, with the brake I36 applied and the circuit to the motor I 32 interrupted. Continued rotation of the cam I43 will then place the cam portion I1I in contact with the roller I44, thereby enabling the spring I49 to actuate the arm I46 to engage the contact I6I with the contact I63, whereupon the relays I15 and I16 are again energized as previously described, to effect release of the brake I36 and complete the circuit to the motor I99. The Micro switch I59 is actuated as an incident to the engagement of the contact I6I with the contact I63 through the actuation of the switch pin I65 by the spring arm I69 so that the contacts I95 and I96 of said switch are closed to thereby complete the circuit to the motor I32. The circuit to the motor I32 is then completed through the main conductor I99, relay contacts I 89 and I99 and wire 292 to motor terminal 29I and from motor terminal 296 through wires 295, 261, Micro switch contacts I95 and I66, wire 298 and through the other main conductor I6I The motor will then be driven in a reverse direction to move the hold-down member III back to its initial-position corresponding to the beginning of a bending operation to be performed upon alength of spring material. The cam portion I'I-I is defined by an arc q which is equal to the are 7 ,380 that the forward and reverse time periods of operation of the motor I32 are identical.

Any conventional cut-off means may be provided to sever the formed spring after the bending operation has been completed. Fig. 18 illustrates in dot-and-dash' lines an anvil 2I0 which may be mounted in any suitable manner upon the bed- I00, and a cooperating cut-off member 2 which maybe reciprocated relative to the anvil 2| by any conventional means. The cut-off member 2| I, of course, is to beautomaticallyop erated in proper timed relation with themovement of other parts of the machine. g In one mode of operation of the machine, the drive rolls I and I06 are rotated only during the portion of the cycle that the motor I 32 is being operated in the forward direction, i. e., advancing the hold-down member I I I toward the die block IIO while the spring material is being bent. This will produce a constant tension spring in which the inner end of the spring is bent upon a greater radius of curvature than the outer end and in which the curvature of the bent portion of the spring progressively decreases from end to end. The operation of the feed rolls I05 and I06 is interrupted after the spring has been completely formed, and during the time that the motor is being driven in a reverse direction to return the hold-down member III to its retracted position preparatory to the bending of' the spring material I09 to form another spring.

Fig. 22 schematically illustrates drive means for. the feed rolls I05, and- I06 andthe control cam I43, whereby the foregoing may be effected. Thus, a gear 2 I 5 is secured to the shaft I0I carrying the feed roll I06, and a gear 2 I6 meshing with the gear 2I5 is secured to'the shaft I04 carrying the other feed roll I05. A large gear 2 I 'I is mounted upon a main drive shaft-2H3, and is provided with teeth '2I9 extending only through half of its circumference, whereby to effectv intermittent driving of the gear 2I6. The shaft 2I8 is journaled in a bracket 2I8? secured to. thebed I00 and may be driven by any suitable, means .(not shown). A stop segment 220 is secured to the gear 2I6 in cooperating relation with a blocker segment 22l carried by the gear 2I0, at the portion of the periphery thereofwhich is devoid of the driving teeth 2I9. A gear22'2 is secured to thedrive shaft 2I8 .and meshes with a gear 223 mounted upon the cam shaft 142;. Thus, the cam shaft I42 is continuously rotated; whereas, the gears 2 I6 and 2I5, which drive thefeed rolls -I05 and I06, are rotated only at such time as theportion of the cam I is engaged with the roller I44 and the hold-down member I I I is being very slowly advanced. The drive arrangement issuch that driving of the gear 2 I6 is'discontinued at the time that the platform II9 reaches the desired advanced position. The blocker segment 22I then cooperates with the stop 220 to hold the gear 2I6 stationary while the cam portion .IHis engaged with the roller I44 to effect driving of -the motor I32 in a reverse directionfto retract the platform I I9 and the hold-down memberI I I carried thereby to its starting position. -Thus,,the feed rolls I05 and I06 are idle while thehold-down member III is being retracted. The-cut-off member 2H may be actuated at anytime during; the interval 18 that the drive of the feed rolls I05 and I06 is interrupted. r j

While spring material I09 is being fed by the feed rolls I05 and I06, the guide means' l I2 will position said spring-material for movement in a path substantially perpendicular to theworking surfaces of the die blocks H0 and III so that as the spring'material is bent and winds itself up into a coil, the several convolutions of the coil will be disposed in a substantially commonradial plane.

While only one set of feed rolls and one guide has been illustrated in the machine disclosed in Figs. 18 and 20, it will be apparent that any number of each may be'employed, so that a plurality of springs may be simultaneously bent, and thus enable the same to be economically and quickly mass-produced in large numbers.

*Fig. 24 illustrates a modified form of cam 230 that may be mounted upon the shaft I42 in lieu of the cam I43 to cause the die block I I Ito be retracted instead'of advanced at the beginning of a bending cycle to produce a spring having different characteristics from that formed under the control of the cam I43. The cam 230 includes two arcuate portions '23I and 232 corresponding to-the portion I'I0 of the cam I43, but which, when engaged with the roller I44, actuate the contact I6I to effect operation of the motor I32 in a reverse direction at that time to retract the die member II I intwo stages from its fully advanced position. The cam230 also includes arcuate portions 233, 234, 235 corresponding to portions I12 and I13, which respectively interrupt the circuit to the motor I32 and apply the brake I36 whenever these portions are engaged with the roller I44. A cam portion 236 disposed between the cam portions 233 and 235 corresponds to the portion III of cam I43 which, when-engaged with the roller I44, effects-drivingof the motor I32 in a forward direction, tothereby advanceand return the platform 9 and the die block III toward their initial starting-position in one stage. a

The cam portions 23 and 232, respectively, extend through anangle of 55 so that the motor I32 isintermittently driven in a'reverse direction through a total angle of of revolution of the cam 230 to gradually retract the die block I I I. I The cam portion 2 3| is effective for a period of time corresponding to an angular movement of 55 of the cam 230, the operation of the motor I 32 being interrupted when the portion 234 of the cam engages with the roller I44, the reverse driving of the motor I32 being continued when the portion 232 of the cam 230 engages with the roller I44 for a period of time corresponding to another 55 0f angularmovement of the cam 230. The driving of the motor I32 is again interrupted when the cam portion 235 engages the roller I44, and its direction of rotation is subsequently changed and it rotates in. a forward direction to return thedie block III toward the die block I I0'when the camiportio'n 236 is engaged with the roller I44. The forward drive continues for a period of time corresponding to a total angular rotation of 110 of the cam 230, so that the die block I IIis returned to exactly thesame position it occupied closeitothe die block I I0 at the beginning; of the spring+forming cycle. The'driving .of the motor, of course, is again interrupted at the end of the cycle. when the cam portion 233 is engaged'with the-roller I44. 'Itj willbe understood that thez-feed rolls I04 and: I 05 feed spring material tothe-die blocks 19 III] and III while the cam portions 23I, 234 and 232 of cam 230 are actively engaged with roller I44, as is done while the cam portion I of cam I43 is active, and that the feed is interrupted before cam portion 236 becomes active.

Fig. schematically illustrates a spring S which can be formed under the control of the cam 230, it being understood that the spacing of the convolutions of said spring has been exaggerated for illustrative purposes. It will be noted that the inner convolutions 240 of the spring are bent upon a uniformly varying but increasing radius, corresponding to the retraction of the die block III during the time that the cam portion 23I is engaged with the roller I44. The intermediate convolutions 24 of the spring are bent upon a constant radius, corresponding to the interval that the portion 234 of the cam is ene se th th r er 1. a d t e c cu t t t motor I32 is interrupted and the die block III i held stationary. The outer convolutions 242 of the spring are bent upon a uniformly varying but increasing radius, corresponding to the period during which the cam portion 232 is engaged with the roller I44 and the motor I32 is slowly moving the die block III away from the die block H0. The varying radius of the outer convolutions 242 is greater than the varying radius of the inner convolutions 240.

It will be understood that other cams, in addition to the cam 23!), can be substituted for the cam I43 and properly timed with the machine cycle to provide coil springs having one or more portions thereof bent upon different constant radii, and/or one or more portions thereof bent upon different varying radii of curvature.

It will also be understood that the automatic control of the motor I32 can be rendered ineffective at any time by manually opening a main switch M, Fig. 23. Thus, if it is desired to form a number of springs by bending the spring material Hi9 upon any desired constant radius for the full length of the springs, then the circuit to the motor I32 can be manually interrupted by opening switch M when the hold-down member III is spaced the correct distance from the die member III) to effect bending of said spring material upon such constant radius of curvature.

It will be apparent from the preceding description that the apparatus and the methods of forming the strips, as well as the characteristics of the resulting springs, may be modified considerably without departing from the invention. Therefore, the forms of the invention described herein should be considered as illustrative and not as limiting the scope of thefollowing claims.

I claim:

1. A coil spring comprising a piece of spring metal having unequally stressed convex and concave surfaces, each increment of said piece transversely of its length having the same radius of curvature, when in repose, said piece being coiled upon itself in a plurality of convolutions disposed in a substantially common radial plane and resisting straightening of said convolutions with constant tension throughout the length of said piece.

2. A constant tension spring, comprising: an elongated piece of material having spring characteristics and having successive increments thereof bent upon a constant radius so that all bent portions thereof normally tendto assume a constant radius of curvature, said piece being wound into coil form with the convolutions thereof lying substantially in a common radial 20 plane, the inherent stress in said bent piece tending to maintain said convolutions in tight contact and non-cumulatively resisting unwinding of the coil.

3. A constant tension spring assembly, comprising: a spring having a plurality of convolutions disposed in a substantially common radial plane, every increment of said convolutions being bent upon the same radius of curvature and equally stressed; and means supporting said spring for free rotation about its axis, whereby pull exerted on the outer end of said spring to partially unwind and straighten said spring is opposed by said equally bent increments of said spring at the point of tangency of the straightened part of said spring with the coiled remainder of said spring.

4. A constant tension spring assembly, comprising: a flexible unwindable and self-winding spring having a plurality of convolutions every portion thereof being bent on the same radius of curvature and equally stressed, said spring having a free end, and means supporting said spring for free rotation, said convolutions of said spring being successively unwindable and straightenable by a force applied to the free end of the spring, said force being opposed by uniform resistance to unwinding offered by any given increment of said spring at the point of tangency of the straightened part of said spring with the uncoiled remainder of said spring, re-.- gardless of the wound and unwound state of said spring.

5. The spring assembly set forth in claim 4 in which said spring is a substantially helical spring.

6. The spring assembly set forth in claim 4, in which each of said convolutions of said spring is free of restraint by the other convolutions during unwinding.

7. The spring assembly set forth in claim 4 in which said means supporting said spring for free rotation comprises a hollow container in which said spring is received and having an opening in one wall thereof through which said spring is withdrawn to unwind it, said spring normally coiling up in said container when relieved of the force applied to said free end.

8. A spring assembly as set forth in claim 4 in which said means supporting said spring for free rotation comprises a rotatable member and means supporting said rotatable member for free rotation, said spring being wound around said rotatable member.

9. A spring assembly comprising: a rotatable member, means rotatably supporting said rotatable member, a coil spring wound in a plurality of superimposed convolutions upon the outer periphery of said rotatable member, the radii of curvatures of all of the convolutions of said coil spring, When in repose, being less than the radius of curvature of the outer periphery of said member, and the radius of curvature of the outermost convolution, when in repose, not exceeding the radius of curvature of the inner-.- most convolution when the latter is in repose.

10. A spring comprising: a plurality of spirally wound convolutions of spring metal, at least a portion of the spring having outermost and innermost convolutions characterized in that the radius'of curvature of the-outermost convolution of said portion, when in repose, does not exceed the radius of curvature of the innermost convolution of said portion, when in repose.

11. A spring assembly, comprising: a plurality of spirally wound convolutions of spring metal, said spring having an outer end, at least a portion of the spring having outermost and innermost convolutions characterized in that the radius of curvature of the outermost convolution of said portion, when in repose, does not exceed the radius of curvature of the innermost convolution of said portion, when in repose; and means supporting said spring for free rotation for unwinding by a force applied to said outer end of said spring to successively unwind and straighten the convolutions of said spring.

12. A spring comprising: a plurality of spirally wound convolutions of spring metal, the radius of curvature of any convolution of said spring, when in repose, not exceeding the radius of curvature of the next adjacent inner convolution of said spring, when in repose.

13. A spring as set forth in claim in which the convolutions of said portion have, when in r pose, the same radius of curvature, and another portion of said spring has convolutions, when in repose, of a varying radius of curvature.

14. A spiral spring comprising: a coiled elongated piece of material having spring characteristics, and having a plurality of convolutions of said material, one portion of said piece having convolutions of which the radius of curvature of the outermost convolution of the portion, when in repose, does not exceed the radius of curvature of the innermost convolution of said portion, and said piece having another portion the successive convolutions of which have a radius of curvature, when in repose, different from the radius of curvature of said innermost convolution of said one portion, when in repose.

15. A flexible unwindable and self-winding spring comprising: a length of spring material formed into a plurality of convolutions and terminating in a free end, the radius of curvature of the convolution nearest said free end, when in repose, being not greater than the radius of curvature of the convolution at the opposite end of said spring, when in repose, said convolutions normally being unwindable and straightenable individually and in succession starting at said free end by a force applied to said free end, said force being opposed by uniform resistance to unwinding regardless of the wound and unwound state of said spring.

16. A spring comprising: two coils connected together each of said coils including a plurality of spirally wound convolutions of spring metal, at least a portion of each coil having outermost and innermost convolutions characterized in that the radius of curvature of the outermost convolution of said portion, when in repose, does not exceed the radius of curvature of the innermost convolution of said portion, when in repose.

17. A spring as defined in claim 16, in which the coils are wound in opposite directions and the outermost convolution of one coil is engaged with the outermost convolution of the other coil, when the spring is in repose.

18. A spring assembly comprising a strip of spring material having its opposite ends formed into coils, each coil containing a plurality of convolutions, at least a portion of each coil having outermost and innermost convolutions characterized in that the radius of curvature of the outermost convolution of said portion, when in repose, does not exceed the radius of curvature of any innermost convolution of said portion, when in repose, and means supporting each coil for independent coiling and uncoiling.

19. A spring assembly comprising a strip of spring material having its opposite ends formed into coils, each coil containing a plurality of convolutions, at least a portion of each coil having outermost and innermost convolutions characterized in that the radius of curvature of the outermost convolution of said portion, when in repose, does not exceed the radius of curvature of the innermost convolution of said portion, when in repose, means supporting each coil for independent coiling and uncoiling, and means connected to at least one of the means supporting each coil and exerting tension thereon tending to move the supporting means apart and uncoil said coils.

BASIL LERMO'NT.

REFERENfiES CITED i'he following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 122,288 Smith Dec. 26, 1871 598,445 Shepherd Feb. 1, 1898 1,207,880 Doerr Dec. 12, 1916 1,258,091 Clark Mar. 5, 1918 1,258,092 Clark Mar. 5, 1918 1,266,070 Sleeper May 14, 1918 1,660,051 Sargent Feb. 21, 1928 1,715,219 Biggert May 28, 1929 1,786,444 Muehlen Dec. 30, 1930 1,871,665 Dallas Aug. 16, 1932 1,895,948 Broek Jan. 31, 1933 1,902,491 Dahl Mar. 21, 1933 1,977,546 Fornelius Oct. 16, 1934 2,038,305 Mikaelson Apr. 21, 1936 2,179,011 Hudson Nov. 7, 1939 2,192,101 Peskin Feb. 27, 1940 2,203,095 Kreissig et a1. June 4, 1940 2,246,239 Brand June 17, 1941 2,265,370 Hennessy Dec. 9, 1941 2,301,960 Lermont Nov. 17, 1942 2,324,115 Schultz July 13, 1943 2,377,950 McMinn June 12, 1945 2,388,537 Hallstrom Nov. 6, 1945 2,457,705 Moran Dec. 28, 1948 2,480,826 Anderson Sept. 6, 1949 FOREIGN PATENTS Number Country Date 94,867 Switzerland May 16, 1922 383,357 Great Britain Nov. 17, 1932 430,457 Great Britain June 19, 1935 787,807 France July 16, 1935 

